EP1930221B1 - Drive control device for vehicle - Google Patents
Drive control device for vehicle Download PDFInfo
- Publication number
- EP1930221B1 EP1930221B1 EP06810824A EP06810824A EP1930221B1 EP 1930221 B1 EP1930221 B1 EP 1930221B1 EP 06810824 A EP06810824 A EP 06810824A EP 06810824 A EP06810824 A EP 06810824A EP 1930221 B1 EP1930221 B1 EP 1930221B1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D29/00—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto
- F02D29/02—Controlling engines, such controlling being peculiar to the devices driven thereby, the devices being other than parts or accessories essential to engine operation, e.g. controlling of engines by signals external thereto peculiar to engines driving vehicles; peculiar to engines driving variable pitch propellers
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/04—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units
- B60W10/06—Conjoint control of vehicle sub-units of different type or different function including control of propulsion units including control of combustion engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W10/00—Conjoint control of vehicle sub-units of different type or different function
- B60W10/10—Conjoint control of vehicle sub-units of different type or different function including control of change-speed gearings
- B60W10/101—Infinitely variable gearings
- B60W10/108—Friction gearings
- B60W10/109—Friction gearings of the toroïd type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60W—CONJOINT CONTROL OF VEHICLE SUB-UNITS OF DIFFERENT TYPE OR DIFFERENT FUNCTION; CONTROL SYSTEMS SPECIALLY ADAPTED FOR HYBRID VEHICLES; ROAD VEHICLE DRIVE CONTROL SYSTEMS FOR PURPOSES NOT RELATED TO THE CONTROL OF A PARTICULAR SUB-UNIT
- B60W30/00—Purposes of road vehicle drive control systems not related to the control of a particular sub-unit, e.g. of systems using conjoint control of vehicle sub-units
- B60W30/18—Propelling the vehicle
- B60W30/188—Controlling power parameters of the driveline, e.g. determining the required power
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
- F16H61/66—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing specially adapted for continuously variable gearings
- F16H61/664—Friction gearings
- F16H61/6648—Friction gearings controlling of shifting being influenced by a signal derived from the engine and the main coupling
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2250/00—Engine control related to specific problems or objectives
- F02D2250/18—Control of the engine output torque
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D31/00—Use of speed-sensing governors to control combustion engines, not otherwise provided for
- F02D31/001—Electric control of rotation speed
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S475/00—Planetary gear transmission systems or components
- Y10S475/904—Particular mathematical equation
Definitions
- the present invention relates to a drive control device for a motor vehicle.
- a control system of Patent Document 1 controls both an input to an engine and a counter torque in a CVT (continuously variable transmission) on the basis of a preliminarily stored engine map.
- the aforementioned CVT is of a torque control type.
- a transmission torque is controlled by pushing and pulling a roller by a hydraulic cylinder for pressing the roller against a disk.
- the transmission torque nonlinearly changes, for example, with respect to a change in the transmission gear ratio of the CVT.
- a plurality of different gains should be selectively employed according to the transmission gear ratio in the control of the hydraulic pressure of the hydraulic cylinder for providing a desired transmission torque.
- a vehicle drive control device comprises a continuously variable transmission mechanism (hereinafter referred to as "CVT") of a torque control type capable of continuously varying a transmission gear ratio, and a controller which controls operations of the CVT and an engine.
- the controller includes a first control section which controls a torque of the CVT based on a target transmission input torque, and a second control section which controls a torque of the engine based on a target engine rotation speed.
- the torque control of the engine and the control of the target transmission input torque equivalent to a torque load to be applied to the engine are employed in combination, thereby permitting an optimum control operation. That is, a relationship between an input and an output can be linearized in the control performed by the CVT torque control section and the control performed by the engine control section, thereby simplifying the control operation. As a result, power train response can be improved at lower costs in a motor vehicle including the CVT of the torque control type.
- IVT infinity variable transmission
- 2 engine
- 5 IVT input shaft
- 6 CVT
- 7 planetary gear mechanism
- 8 IVT output shaft
- 9 CVT input shaft
- 10 CVT output shaft
- 17 carriage
- 18 hydraulic chamber
- 19 hydraulic cylinder
- 20 first hydraulic chamber
- 21 second hydraulic chamber
- 27 power circulation mode clutch
- 29 direct mode clutch
- 31 first pressure control valve
- 33 second pressure control valve
- 34 controller (controller for controlling operations of CVT and engine)
- 35 accelerator operation amount sensor
- 36 vehicle speed sensor
- 37 engine rotation speed sensor
- 38 CVT input shaft rotation speed sensor
- 39 CVT output shaft rotation speed sensor
- 40 pressure sensor
- 41 fuel supply amount adjusting mechanism
- 42 driver's demand converting section
- 43 IVT control section (first control section )
- 43A CVT control section (first control section )
- 44 engine control section (second control section)
- 46 target vehicle speed computing section
- 47 target
- FIG. 1 is a schematic diagram schematically showing the construction of a vehicle drive control device according to one embodiment of the present invention.
- an infinitely variable transmission 1 (hereinafter referred to as "IVT 1") includes an IVT input shaft 5 coupled to an output shaft 3 of an engine 2 through a torsion damper 4, a CVT 6 of a full-toroidal continuously variable transmission, a planetary gear mechanism 7, and an IVT output shaft 8 provided parallel to the IVT input shaft 5 and coupled to drive wheels.
- the CVT 6 is of a so-called torque control type.
- the CVT 6 includes a CVT input shaft 9 provided coaxially with the IVT input shaft 5, and a hollow CVT output shaft 10 through which the CVT input shaft 9 is inserted.
- a pair of input disks 11, 12 are provided corotatably with the CVT input shaft 9. These input disks 11, 12 are positioned back to back, and are each formed with a toroidal race. Further, a pair of output disks 13, 14 each formed with a toroidal race opposed to the toroidal race of the corresponding input disk 11, 12 are provided corotatably with the CVT output shaft 10.
- Rollers 15, 16 for torque transmission between the disks 11 and 13 and between the disks 12 and 14 are provided between the toroidal races of the input disks 11, 12 and the output disks 13, 14. A torque from the input disk 11 is transmitted to the output disk 13 through the rollers 15, while a torque from the input disk 12 is transmitted to the output disk 14 through the rollers 16.
- the rollers 15, 16 are each supported by a carriage 17.
- the axis of the carriage 17 extends perpendicularly to the rotation axis of each of the rollers 16 and forms a predetermined caster angle ⁇ with respect to the rotation axis as shown in Fig. 2 , though schematically illustrated in Fig. 1 . This is true for the rollers 15 and the carriages 17 respectively supporting the rollers 15.
- a terminal load is applied to each of the disks 11, 13; 12, 14 by a hydraulic pressure of a hydraulic chamber 18.
- the rollers 15, 16 each receive a biasing force generated by a pressure difference between first and second hydraulic chambers 20, 21 of a hydraulic cylinder 19 via the carriage 17 to be thereby pressed against the disks 11, 13; 12, 14.
- the rollers 15, 16 each supported by the carriage 17 are tilted so that the rotation axes of the rollers 15, 16 each form an oscillation angle about the axis of the carriage 17 to eliminate imbalance between reaction forces occurring in the carriages 17 due to the torque transmission and torques required for driving the output disks 13, 14. This changes the attitudes of the rollers 15, 16 to continuously vary the speed ratios between the disks 11 and 13 and between the disks 12 and 14.
- the planetary gear mechanism 7 includes a sun gear 22, a plurality of planetary gears 24 supported by a carrier 23, and a ring gear 25 having inner teeth meshed with the planetary gears 24.
- the planetary gear mechanism 7 is disposed between the CVT input shaft 9 and the CVT output shaft 10. More specifically, the ring gear 25 is coupled corotatably with the IVT output shaft 8.
- the rotation of the CVT input shaft 9 is transmitted to the carrier 23 through a gear train 26 and a power circulation mode clutch 27 (also referred to as "low clutch”) in a coupled state.
- the gear train 26 includes a gear 26a coupled corotatably with the CVT input shaft 9, and a gear 26b meshed with the gear 26a and rotatably supported by the IVT output shaft 8.
- the power circulation mode clutch 27 is, for example, a multi-plate clutch which is capable of coupling and decoupling the gear 26b with the carrier 23.
- the power circulation mode clutch 27 permits a power circulation mode, when being coupled, in which the power transmission is achieved within a transmission gear ratio range including an infinite gear ratio.
- the rotation of the CVT output shaft 10 is transmitted to the sun gear 22 through a gear train 28.
- the gear train 28 includes a gear 28a coupled corotatably with the CVT output shaft 10, and a gear 28b meshed with the gear 28a and coupled corotatably with the sun gear 22.
- a direct mode clutch 29 (also referred to as "high clutch") capable of coupling and decoupling the gear 28b with the IVT output shaft 8 is disposed between the gear 28b and the IVT output shaft 8.
- the direct mode clutch 29 permits a direct mode, when being coupled, in which the power transmission is achieved by the CVT 6 alone.
- the engine power is outputted to the IVT output shaft 8 and circulated through the CVT 6 and the planetary gear mechanism 7 in the so-called power circulation mode.
- the power circulation mode is selected when a greater drive torque is required, for example, when the motor vehicle is started, driven at a lower speed, or rapidly accelerated during medium speed traveling.
- the power circulation mode clutch 27 being decoupled and with the direct mode clutch 29 being coupled, on the other hand, the power of the engine 2 is transmitted to the sun gear 22 through the CVT 6, and outputted from the IVT output shaft 8 through the direct mode clutch 29 in the direct mode.
- the direct mode is selected when a greater drive torque is not required, for example, when the motor vehicle travels at a medium speed or accelerated during high speed traveling.
- a hydraulic pressure from a first pump 30 is controlled by a first pressure control valve 31, and applied to the hydraulic chamber 18 for the terminal load and to the first hydraulic chamber 20 of the hydraulic cylinder 19.
- a hydraulic pressure from a second pump 32 is controlled by a second pressure control valve 33, and applied to the second hydraulic chamber 21 of the hydraulic cylinder 19.
- a controller 34 which controls the operations of the IVT 1 and the engine 2 is an electronic control unit (ECU).
- the controller 34 is connected to an accelerator operation amount sensor 35 which detects an accelerator operation amount, a vehicle speed sensor 36 which detects a vehicle traveling speed, an engine rotation speed sensor 37, a CVT input shaft rotation speed sensor 38 which detects the rotation speed of the CVT input shaft 9, a CVT output shaft rotation speed sensor 39 which detects the rotation speed of the CVT output shaft 10, a pressure sensor 40 serving as pressure detecting means which detects a pressure difference P between the first hydraulic chamber 20 and the second hydraulic chamber 21 of the hydraulic cylinder 19, and an IVT output shaft rotation speed sensor 75 which detects the rotation speed of the IVT output shaft 8. Signals from these sensors 36 to 40 and 75 are inputted to the controller 34.
- the controller 34 To control an engine output, the controller 34 outputs a command signal to a fuel supply amount adjusting mechanism 41 which adjusts the amount of a fuel to be supplied to the engine 2. Further, the controller 34 outputs command signals to the first pressure control valve 31 and the second pressure control valve 33 to control the torque transmission capabilities of the rollers 15, 16. In addition, the controller 34 outputs coupling/decoupling command signals (see Fig. 3 ) to the power circulation mode clutch 27 and the direct mode clutch 29 for switching between the power circulation mode and the direct mode.
- the controller 34 includes a plurality of functional sections which are implemented on a software basis by causing a computer to perform predetermined program processes. That is, the controller 34 includes a driver's demand converting section 42, an IVT control section 43 serving as a first control section, and an engine control section 44 serving as a second control section for controlling the engine 2.
- the driver's demand converting section 42 determines a state quantity for achieving a vehicle driving state demanded by the driver.
- the IVT control section 43 has the function of controlling the torque of the CVT 6, and the function of switching a mode between the power circulation mode and the direct mode.
- the driver's demand converting section 42 computes a target engine rotation speed ⁇ e,T and a target transmission input torque T TRN,T as state quantities which impart the engine 2 with a maximum efficiency on the basis of the accelerator operation amount ⁇ and the vehicle speed V.
- the IVT control section 43 With inputs of the target transmission input torque T TRN,T applied from the driver's demand converting section 42, the CVT input shaft rotation speed ⁇ i detected by the CVT input shaft rotation speed sensor 38, the CVT output shaft rotation speed ⁇ 0 detected by the CVT output shaft rotation speed sensor 39 and the pressure difference P detected by the pressure sensor 40, the IVT control section 43 outputs command signals, for example, to solenoids of the first and second pressure control valves 31, 33 on the basis of the target transmission input torque T TRN,T , the CVT input shaft rotation speed ⁇ i , the CVT output shaft rotation speed ⁇ 0 and the pressure difference P.
- the IVT control section 43 With inputs of the CVT input shaft rotation speed ⁇ i (corresponding to the IVT input shaft rotation speed) detected by the CVT input shaft rotation speed sensor 38 and the IVT output shaft rotation speed ⁇ IVT,o detected by the IVT output shaft rotation speed sensor 75, the IVT control section 43 further outputs the coupling/decoupling command signals for the mode switching to the power circulation mode clutch 27 and the direct mode clutch 29 on the basis of the CVT input shaft rotation speed ⁇ i and the IVT output shaft rotation speed ⁇ IVT,o .
- the engine control section 44 outputs a valve aperture command signal, for example, to a solenoid of a throttle aperture adjusting valve serving as the fuel supply amount adjusting mechanism 41 on the basis of the target engine rotation speed ⁇ e,T , the engine rotation speed ⁇ e , the CVT input shaft rotation speed ⁇ i , the CVT output shaft rotation speed ⁇ o and the pressure difference P.
- the driver's demand converting section 42 includes a target engine output computing section 45, a target vehicle speed computing section 46, a target vehicle speed correcting section 47 and a state quantity computing section 48.
- the target engine output computing section 45 computes a target engine output P e,T by employing a first engine map 71 preliminarily stored.
- the first engine map 71 is a map in which engine output levels P for accelerator operation amounts ⁇ and vehicle speed levels V are preliminarily stored.
- the target vehicle speed computing section 46 computes a target vehicle speed V T by employing a second engine map 72 preliminarily stored.
- the second engine map 72 is a map in which relationships between the engine rotation speed ⁇ e and an engine torque Te which achieve the maximum efficiency for engine output levels Pe are stored as a peak efficiency curve (PEC).
- the computed target vehicle speed V T is outputted to the target vehicle speed correcting section 47.
- the target vehicle speed correcting section 47 determines a corrected target vehicle speed V AT by causing a control gain multiplying section 49 to multiply a difference (V T -V) between the target vehicle speed V T and the actual vehicle speed V detected by the vehicle speed sensor 36 by a control gain k1 and adding the resulting correction amount k1 ⁇ (V T -V) to the target vehicle speed V T .
- the corrected target vehicle speed V AT thus obtained is outputted to the state quantity computing section 48.
- the state quantity computing section 48 computes a target engine rotation speed ⁇ e,T and a target transmission input torque T TRN,T , on the basis of the corrected target vehicle speed V AT , which impart the engine 2 with the maximum efficiency.
- the state quantity computing section 48 includes a post-correction target engine output computing section 50, a target engine rotation speed/target engine torque computing section 51 serving as a target engine performance computing section, and a target transmission input torque computing section 52.
- the post-correction target engine output computing section 50 computes a post-correction target engine output P e,AT for the corrected target vehicle speed V AT by employing the aforementioned first engine map 71. That is, a boosted target engine output is provided.
- the computed post-correction target engine output P e,AT is outputted to the target engine rotation speed/target engine torque computing section 51.
- the target engine rotation speed/target engine torque computing section 51 computes the target engine rotation speed ⁇ e,T and a target engine torque T e,T by employing the aforementioned second engine map 72.
- the computation of the target engine rotation speed ⁇ e,T and the target engine torque T e,T is based on the peak efficiency curve (PEC), thereby making it possible to effectively perform the drive control for improving the mileage without impairing the acceleration performance.
- the target engine rotation speed ⁇ e,T and the target engine torque T e,T computed by the target engine rotation speed/target engine torque computing section 51 are outputted to the target transmission input torque computing section 52, while the computed target engine rotation speed ⁇ e,T is outputted to the engine control section 44.
- the target transmission input torque computing section 52 computes the target transmission input torque T TRN,T by employing the following expression (2):
- the IVT control section 43 includes a real transmission input torque computing section 53, a target transmission input torque correcting section 54 serving as a CVT torque control section, a demanded pressure difference computing section 55, a signal outputting section 56 and a mode switching section 76.
- the mode switching section 76 computes an IVT gear ratio on the basis of the CVT input shaft rotation speed ⁇ i (equivalent to the IVT input shaft rotation speed) detected by the CVT input shaft rotation speed sensor 38 and the IVT output shaft rotation speed ⁇ IVT,o detected by the IVT output shaft rotation speed sensor 75, and outputs the coupling/decoupling command signals to the power circulation mode clutch 27 and the direct mode clutch 29 on the basis of the computed IVT gear ratio for the mode switching.
- the real transmission input torque computing section 53 computes a real transmission input torque T TRN,R (for the direct mode) on the basis of the following expression (3):
- T TRN , R kr ⁇ Rv / Rv - 1 ⁇ P
- the signal outputting section 56 converts the demanded pressure difference P D into a voltage command signal, and outputs the voltage command signal to the solenoids of the first pressure control valve 31 and the second pressure control valve 33.
- desired reaction forces are applied to the rollers 15, 16 to transmit a desired transmission torque to the CVT 6.
- the engine control section 44 includes a real transmission input torque computing section 59, a demanded engine torque setting section 60 and a signal outputting section 61.
- the real transmission input torque computing section 59 computes the real transmission input torque T TRN,R on the basis of the above expression (3) .
- the computed real transmission input torque T TRN,R is outputted to the demanded engine torque computing ⁇ setting ⁇ section 60.
- the signal outputting section 61 converts the demanded engine torque T e,D into a voltage command signal, and outputs a voltage command signal, for example, to the solenoid of the throttle valve aperture adjusting electromagnetic valve serving as the fuel supply amount adjusting mechanism 41.
- This imparts the engine 2 with a desired dynamic characteristic.
- the control of the torque of the engine 2 is combined with the control of the transmission input torque which is a torque load exerted on the engine 2. This permits an optimum control operation. In other words, the optimum control operation is achieved by adding the control of the load torque exerted on the engine through the CVT 6 of the torque control type to the engine control.
- the relationship between the input and the output is linearized in the control by the IVT control section 43 and the control by the engine control section 44, thereby simplifying the control operation.
- the power flow of the system is controlled by combining the torque control of the CVT 6 performed by the IVT control section 43 with the torque control of the engine 2 performed by the engine control section 44, and the above expression (6-1) based on the Newton' s second law is employed as a control rule.
- This makes it possible to determine the demanded engine torque T e,D without consideration of the vehicle inertia and adjust the engine output on the basis of the demanded engine torque T e,D .
- the power flow from the engine 2 to the drive wheels (positive flow with the engine torque T e kept at a higher level than the real transmission input torque T TRN,R , T e > T TRN,R ) can be maintained in a transient drive control operation. That is, a so-called NMP (non-minimum phase) phenomenon can be prevented in which the rotation speed of the vehicle wheels otherwise initially suffers from undershoot in response to depression of an accelerator pedal. As a result, the drivability and the mileage are improved.
- NMP non-minimum phase
- the IVT control section 43 employs the single control gain k2 for the torque control of the CVT 6 and the engine control section 44 employs the single control gain k3 for the torque control of the engine 2, the control operation is simple and less expensive.
- the engine control section 44 serves to separate the engine response from the input torque (load) of the CVT 6 to linearize the engine speed response so that the response of the system linearly or monotonically increases (or decreases). This is advantageous in that the response of the rotation speed ⁇ e of the engine 2 and the response of the rotation speed of the vehicle wheels (substantially equivalent to the vehicle speed V) are stabilized irrespective of the control gains k2, k3.
- a driver's demand applied to the motor vehicle through the accelerator pedal is converted into the state quantities, i.e., the target engine rotation speed ⁇ e,T and the target transmission input torque T TRN,T , which impart the engine 2 with the maximum efficiency, by the function of the driver's demand converting section 42.
- the engine 2 can be operated at the highest possible efficiency according to the driver's demand without impairing the acceleration performance of the motor vehicle.
- the mileage and the drivability are well-balanced.
- the target vehicle speed correcting section 47 corrects the target vehicle speed V T on the basis of the comparison between the target vehicle speed V T and the actual vehicle speed V, whereby the engine power is artificially boosted according to the driver's demand.
- the target vehicle speed V T is corrected by comparing the actual vehicle speed V with the target vehicle speed V T , more specifically, by employing the difference (V T - V) between the target vehicle speed V T and the actual vehicle speed V, so that the size of a control loop can be reduced.
- the correction amount k1 ⁇ (V T - V) determined by multiplying the difference (V T -V) between the target vehicle speed V T and the actual vehicle speed V by the predetermined gain k1 is added to the target vehicle speed V T to provide the corrected target vehicle speed V AT . Since the single gain k1 is thus employed, the tuning of transient characteristics is facilitated in the power control of the engine 2. Further, the control loop is simple and less expensive. In other words, a transmission kick-down function can be provided at lower costs.
- the target vehicle speed V T is corrected according to the driver's demand, and the target engine output is corrected on the basis of the corrected target vehicle speed V AT . Therefore, the engine output is boosted according to the driver's demand.
- the target level of the engine output to be boosted (the target engine rotation speed ⁇ e,T and the target engine torque T e,T ) is computed on the basis of the peak efficiency curve (PEC) for the relationship between the engine rotation speed ⁇ e and the engine torque T e . This effectively improves the mileage without impairing the acceleration performance.
- Figs. 7 to 10 illustrate another embodiment of the present invention. This embodiment is directed to a vehicle drive control device including a CVT of a torque control type which does not constitute an IVT, while the previous embodiment of Figs. 1 to 6 is directed to the vehicle drive control device having the IVT.
- this embodiment principally differs from the embodiment of Fig. 1 in that the planetary gear mechanism 7, the IVT output shaft 8, the gear trains 26, 28, the power circulation mode clutch 27, the direct mode clutch 29 and the IVT output shaft rotation speed sensor 75 are eliminated.
- a CVT output shaft 10 is coupled to drive wheels 83 through a gear train 80, a differential device 81 and a drive shaft 82.
- the gear train 80 includes a gear 80a corotatable with the CVT output shaft 10, and a gear 80b meshed with the gear 80a and corotatable with a case of the differential device 81.
- a controller 34A of this embodiment principally differs from the controller 34 of the embodiment of Fig. 3 in that a CVT control section 43A is provided instead of the IVT control section 43.
- a target transmission input torque T TRN,T to be applied to the CVT control section 43A from a driver's demand converting section 42 is equivalent to a target CVT input torque.
- the target transmission input torque T TRN,T is computed by a target transmission input torque computing section 52 of the driver's demand converting section 42 of the controller 34A of this embodiment, and applied to the CVT control section 43A.
- the CVT control section 43A of this embodiment principally differs from the IVT control section 43 of Fig. 5 in that the mode switching section 76 is eliminated.
- a real transmission input torque T TRN,R computed by a real transmission input torque computing section 53 of Fig. 10 is equivalent to the real CVT input torque (actual CVT input torque).
- an engine control section 44 has the same construction as in the embodiment of Fig. 6 .
- This embodiment provides the same functions and effects as the embodiment of Figs. 1 to 6 , so that the mileage and the drivability are well-balanced.
- the planetary gear mechanism 7 is simply required to include an element coupled to the CVT input shaft 9, an element coupled to the CVT output shaft 10 and an element coupled to the drive wheels. Further, at least one of the gear trains 26, 28 may be replaced with a chain sprocket mechanism.
- the type of the CVT is not limited to the full-toroidal type, but may be a half-toroidal type or any other type such as a belt type or a chain type.
- the engine output was boosted with the control gain k1 set at a relatively low level in the target vehicle speed correcting section 47 of Fig. 4 in Example 1, and the engine output was boosted with the control gain k1 set at a relatively high level in Example 2.
- the target vehicle speed correcting section was eliminated.
- a simulation was performed to determine a response time from the operation of the accelerator pedal to the start of a vehicle speed change. The results are shown in Fig. 11 .
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- General Engineering & Computer Science (AREA)
- Transportation (AREA)
- Automation & Control Theory (AREA)
- Control Of Transmission Device (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
Description
- The present invention relates to a drive control device for a motor vehicle.
- In a motor vehicle, a driver operates an accelerator pedal to demand engine power. If the diver feels insufficient acceleration, the driver further depresses the accelerator pedal. The rotation speed of vehicle wheels (equivalent to a vehicle speed) is responsive to the operation of the accelerator pedal.
A control system ofPatent Document 1 controls both an input to an engine and a counter torque in a CVT (continuously variable transmission) on the basis of a preliminarily stored engine map. - Patent Document 1: Japanese Unexamined Patent Publication No.
7-505699 (1995 -
Document GB 1 525 861 claim 1 in a similar control system. - The aforementioned CVT is of a torque control type. In the case of the torque control type, a transmission torque is controlled by pushing and pulling a roller by a hydraulic cylinder for pressing the roller against a disk. The transmission torque nonlinearly changes, for example, with respect to a change in the transmission gear ratio of the CVT.
As a result, a plurality of different gains should be selectively employed according to the transmission gear ratio in the control of the hydraulic pressure of the hydraulic cylinder for providing a desired transmission torque. - This complicates computations to be performed in an ECU (Electronic Control Unit), resulting in difficulty in improving power train response. Further, higher costs are required for the tuning and calibration of the control system.
It is therefore an object of the present invention to provide a vehicle drive control device which is less expensive and excellent in responsiveness. - According to a preferred embodiment of the present invention to achieve the aforementioned object, a vehicle drive control device comprises a continuously variable transmission mechanism (hereinafter referred to as "CVT") of a torque control type capable of continuously varying a transmission gear ratio, and a controller which controls operations of the CVT and an engine. The controller includes a first control section which controls a torque of the CVT based on a target transmission input torque, and a second control section which controls a torque of the engine based on a target engine rotation speed.
- In this embodiment, the torque control of the engine and the control of the target transmission input torque equivalent to a torque load to be applied to the engine are employed in combination, thereby permitting an optimum control operation. That is, a relationship between an input and an output can be linearized in the control performed by the CVT torque control section and the control performed by the engine control section, thereby simplifying the control operation. As a result, power train response can be improved at lower costs in a motor vehicle including the CVT of the torque control type.
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Fig. 1 is a schematic diagram schematically showing the construction of a motor vehicle employing a vehicle drive control device according to one embodiment of the present invention. -
Fig. 2 is a schematic diagram of major portions of a CVT. -
Fig. 3 is a block diagram schematically showing the construction of a controller. -
Fig. 4 is a block diagram schematically showing the construction of a driver's demand converting section. -
Fig. 5 is a block diagram schematically showing the construction of an IVT control section. -
Fig. 6 is a block diagram schematically showing the construction of an engine control section. -
Fig. 7 is a schematic diagram schematically showing the construction of a motor vehicle employing a vehicle drive control device according to another embodiment of the present invention. -
Fig. 8 is a block diagram schematically showing the construction of a controller in the embodiment ofFig. 7 . -
Fig. 9 is a block diagram schematically showing the construction of a driver's demand converting section in the embodiment ofFig. 7 . -
Fig. 10 is a block diagram schematically showing the construction of a CVT in the embodiment ofFig. 7 . -
Fig. 11 is a graph showing a relationship between a vehicle speed level and a response time from the operation of an accelerator pedal to the start of a vehicle speed change. - 1: IVT (infinity variable transmission), 2: engine, 5: IVT input shaft, 6: CVT, 7: planetary gear mechanism, 8: IVT output shaft, 9: CVT input shaft, 10: CVT output shaft, 11,12: input disks, 13,14: output disks, 15,16: rollers, 17: carriage, 18: hydraulic chamber, 19: hydraulic cylinder, 20: first hydraulic chamber, 21: second hydraulic chamber, 27: power circulation mode clutch, 29: direct mode clutch, 31: first pressure control valve, 33: second pressure control valve, 34: controller (controller for controlling operations of CVT and engine), 35: accelerator operation amount sensor, 36: vehicle speed sensor, 37: engine rotation speed sensor, 38: CVT input shaft rotation speed sensor, 39: CVT output shaft rotation speed sensor, 40: pressure sensor, 41: fuel supply amount adjusting mechanism, 42: driver's demand converting section, 43: IVT control section (first control section ), 43A: CVT control section (first control section ), 44: engine control section (second control section), 46: target vehicle speed computing section, 47: target vehicle speed correcting section, 48: state quantity computing section, 51: target engine rotation speed/target engine torque computing section, 52: target transmission input torque computing section, 54: target transmission input torque correcting section, 55: demanded pressure difference setting section, 59: real transmission input torque computing section, 60: demanded engine torque setting section, PD: demanded pressure difference, TTRN,T: target transmission input torque, TTRN,AT: corrected target transmission input torque, TTRN,R: real transmission input torque (actual transmission input torque), Rv: CVT gear ratio, ωi: CVT input shaft rotation speed, ωo: CVT output shaft rotation speed, Te: engine torque, Te,D: demanded engine torque, Ie: engine inertia, ωe,T: target engine rotation speed, ωe: actual engine rotation speed, k3: control gain, θ: accelerator operation amount, V: vehicle speed
- Preferred embodiments of the present invention will be described with reference to the attached drawings.
Fig. 1 is a schematic diagram schematically showing the construction of a vehicle drive control device according to one embodiment of the present invention. Referring toFig. 1 , an infinitely variable transmission 1 (hereinafter referred to as "IVT 1") includes anIVT input shaft 5 coupled to anoutput shaft 3 of anengine 2 through atorsion damper 4, a CVT 6 of a full-toroidal continuously variable transmission, aplanetary gear mechanism 7, and anIVT output shaft 8 provided parallel to theIVT input shaft 5 and coupled to drive wheels. The CVT 6 is of a so-called torque control type. - In this embodiment, the vehicle drive control device including the IVT 1 will be described, but the present invention is applicable to any vehicle drive control device including a CVT of a torque control type.
The CVT 6 includes aCVT input shaft 9 provided coaxially with theIVT input shaft 5, and a hollowCVT output shaft 10 through which theCVT input shaft 9 is inserted. A pair ofinput disks CVT input shaft 9. Theseinput disks output disks corresponding input disk CVT output shaft 10. -
Rollers disks disks input disks output disks input disk 11 is transmitted to theoutput disk 13 through therollers 15, while a torque from theinput disk 12 is transmitted to theoutput disk 14 through therollers 16. Therollers carriage 17. The axis of thecarriage 17 extends perpendicularly to the rotation axis of each of therollers 16 and forms a predetermined caster angle β with respect to the rotation axis as shown inFig. 2 , though schematically illustrated inFig. 1 . This is true for therollers 15 and thecarriages 17 respectively supporting therollers 15. - A terminal load is applied to each of the
disks hydraulic chamber 18. On the other hand, therollers hydraulic chambers hydraulic cylinder 19 via thecarriage 17 to be thereby pressed against thedisks
Therollers carriage 17 are tilted so that the rotation axes of therollers carriage 17 to eliminate imbalance between reaction forces occurring in thecarriages 17 due to the torque transmission and torques required for driving theoutput disks rollers disks disks - The
planetary gear mechanism 7 includes asun gear 22, a plurality ofplanetary gears 24 supported by acarrier 23, and a ring gear 25 having inner teeth meshed with theplanetary gears 24.
Theplanetary gear mechanism 7 is disposed between theCVT input shaft 9 and theCVT output shaft 10. More specifically, the ring gear 25 is coupled corotatably with theIVT output shaft 8.
The rotation of theCVT input shaft 9 is transmitted to thecarrier 23 through agear train 26 and a power circulation mode clutch 27 (also referred to as "low clutch") in a coupled state. Thegear train 26 includes agear 26a coupled corotatably with theCVT input shaft 9, and agear 26b meshed with thegear 26a and rotatably supported by theIVT output shaft 8. The powercirculation mode clutch 27 is, for example, a multi-plate clutch which is capable of coupling and decoupling thegear 26b with thecarrier 23. The powercirculation mode clutch 27 permits a power circulation mode, when being coupled, in which the power transmission is achieved within a transmission gear ratio range including an infinite gear ratio. - The rotation of the
CVT output shaft 10 is transmitted to thesun gear 22 through agear train 28. Thegear train 28 includes agear 28a coupled corotatably with theCVT output shaft 10, and agear 28b meshed with thegear 28a and coupled corotatably with thesun gear 22. A direct mode clutch 29 (also referred to as "high clutch") capable of coupling and decoupling thegear 28b with theIVT output shaft 8 is disposed between thegear 28b and theIVT output shaft 8. The direct mode clutch 29 permits a direct mode, when being coupled, in which the power transmission is achieved by the CVT 6 alone. - With the direct mode clutch 29 being decoupled and with the power
circulation mode clutch 27 being coupled, the power of theengine 2 is transmitted to thecarrier 23 through theIVT input shaft 5 and thegear train 26. As a result, a torque is amplified and transmitted by the ring gear 25 of theplanetary gear mechanism 7, and outputted to theIVT output shaft 8.
At this time, a reaction force occurring due to a drive load exerted on the ring gear 25 also exerts a torque on thesun gear 22. The torque acting on thesun gear 22 is fed back to the CVT 6 through thegear train 28 and theCVT output shaft 10, and transmitted together with the torque outputted from theengine 2 on the side of theCVT input shaft 9 again to thecarrier 23 through thegear train 26 and the powercirculation mode clutch 27. - That is, the engine power is outputted to the
IVT output shaft 8 and circulated through the CVT 6 and theplanetary gear mechanism 7 in the so-called power circulation mode. The power circulation mode is selected when a greater drive torque is required, for example, when the motor vehicle is started, driven at a lower speed, or rapidly accelerated during medium speed traveling.
With the powercirculation mode clutch 27 being decoupled and with the direct mode clutch 29 being coupled, on the other hand, the power of theengine 2 is transmitted to thesun gear 22 through the CVT 6, and outputted from theIVT output shaft 8 through the direct mode clutch 29 in the direct mode. The direct mode is selected when a greater drive torque is not required, for example, when the motor vehicle travels at a medium speed or accelerated during high speed traveling. - A hydraulic pressure from a
first pump 30 is controlled by a firstpressure control valve 31, and applied to thehydraulic chamber 18 for the terminal load and to the firsthydraulic chamber 20 of thehydraulic cylinder 19. A hydraulic pressure from asecond pump 32 is controlled by a secondpressure control valve 33, and applied to the secondhydraulic chamber 21 of thehydraulic cylinder 19.
Acontroller 34 which controls the operations of theIVT 1 and theengine 2 is an electronic control unit (ECU). - The
controller 34 is connected to an acceleratoroperation amount sensor 35 which detects an accelerator operation amount, avehicle speed sensor 36 which detects a vehicle traveling speed, an enginerotation speed sensor 37, a CVT input shaftrotation speed sensor 38 which detects the rotation speed of theCVT input shaft 9, a CVT output shaftrotation speed sensor 39 which detects the rotation speed of theCVT output shaft 10, apressure sensor 40 serving as pressure detecting means which detects a pressure difference P between the firsthydraulic chamber 20 and the secondhydraulic chamber 21 of thehydraulic cylinder 19, and an IVT output shaftrotation speed sensor 75 which detects the rotation speed of theIVT output shaft 8. Signals from thesesensors 36 to 40 and 75 are inputted to thecontroller 34. - To control an engine output, the
controller 34 outputs a command signal to a fuel supplyamount adjusting mechanism 41 which adjusts the amount of a fuel to be supplied to theengine 2. Further, thecontroller 34 outputs command signals to the firstpressure control valve 31 and the secondpressure control valve 33 to control the torque transmission capabilities of therollers controller 34 outputs coupling/decoupling command signals (seeFig. 3 ) to the powercirculation mode clutch 27 and thedirect mode clutch 29 for switching between the power circulation mode and the direct mode. - Referring to
Fig. 3 , thecontroller 34 includes a plurality of functional sections which are implemented on a software basis by causing a computer to perform predetermined program processes. That is, thecontroller 34 includes a driver'sdemand converting section 42, anIVT control section 43 serving as a first control section, and anengine control section 44 serving as a second control section for controlling theengine 2. The driver'sdemand converting section 42 determines a state quantity for achieving a vehicle driving state demanded by the driver. TheIVT control section 43 has the function of controlling the torque of the CVT 6, and the function of switching a mode between the power circulation mode and the direct mode. - With inputs of the accelerator operation amount θ detected by the accelerator
operation amount sensor 35 and the vehicle speed V detected by thevehicle speed sensor 36, the driver'sdemand converting section 42 computes a target engine rotation speed ωe,T and a target transmission input torque TTRN,T as state quantities which impart theengine 2 with a maximum efficiency on the basis of the accelerator operation amount θ and the vehicle speed V.
With inputs of the target transmission input torque TTRN,T applied from the driver'sdemand converting section 42, the CVT input shaft rotation speed ωi detected by the CVT input shaftrotation speed sensor 38, the CVT output shaft rotation speed ω0 detected by the CVT output shaftrotation speed sensor 39 and the pressure difference P detected by thepressure sensor 40, theIVT control section 43 outputs command signals, for example, to solenoids of the first and secondpressure control valves rotation speed sensor 38 and the IVT output shaft rotation speed ωIVT,o detected by the IVT output shaftrotation speed sensor 75, theIVT control section 43 further outputs the coupling/decoupling command signals for the mode switching to the powercirculation mode clutch 27 and the direct mode clutch 29 on the basis of the CVT input shaft rotation speed ωi and the IVT output shaft rotation speed ωIVT,o. - With inputs of the target engine rotation speed ωe,T applied from the driver's
demand converting section 42, the engine rotation speed ωe detected by the enginerotation speed sensor 37, the CVT input shaft rotation speed ωi detected by the CVT input shaftrotation speed sensor 38, the CVT output shaft rotation speed ω0 detected by the CVT output shaftrotation speed sensor 39 and the pressure difference P detected by thepressure sensor 40, theengine control section 44 outputs a valve aperture command signal, for example, to a solenoid of a throttle aperture adjusting valve serving as the fuel supplyamount adjusting mechanism 41 on the basis of the target engine rotation speed ωe,T, the engine rotation speed ωe, the CVT input shaft rotation speed ωi, the CVT output shaft rotation speed ωo and the pressure difference P. - Referring to
Fig. 4 , the driver'sdemand converting section 42 includes a target engineoutput computing section 45, a target vehiclespeed computing section 46, a target vehicle speed correcting section 47 and a state quantity computing section 48. With an input of the accelerator operation amount θ detected by the acceleratoroperation amount sensor 35, the target engineoutput computing section 45 computes a target engine output Pe,T by employing afirst engine map 71 preliminarily stored. Thefirst engine map 71 is a map in which engine output levels P for accelerator operation amounts θ and vehicle speed levels V are preliminarily stored. - With an input of the target engine output Pe,T, the target vehicle
speed computing section 46 computes a target vehicle speed VT by employing asecond engine map 72 preliminarily stored. Thesecond engine map 72 is a map in which relationships between the engine rotation speed ωe and an engine torque Te which achieve the maximum efficiency for engine output levels Pe are stored as a peak efficiency curve (PEC). - It is herein assumed that Pv is vehicle drive power, ηPWT is a drive train efficiency, TRL is a vehicle traveling resistance, and ωW is a drive wheel rotation speed. Then, the vehicle drive power PV is equal to the product of the engine output Pe and the drive train efficiency ηPWT, and equal to the product of the vehicle traveling resistance TRL and the drive wheel rotation speed ωW. That is, an expression PV = Pe × ηPWT = TRL × ωW is established.
Here, the vehicle traveling resistance TRL is expressed as a function TRL(ωw) of the drive wheel rotation speed ωW. That is, an expression TRL = TRL(ωW) is established. Therefore, the drive wheel rotation speed ωW can be expressed as a function of the engine output Pe. That is, an expression ωW = ωW(Pe) is established. Therefore, the target drive wheel rotation speed, i.e., the target vehicle speed VT, can be determined by employing thesecond engine map 72 and the target engine output Pe,T. - The computed target vehicle speed VT is outputted to the target vehicle speed correcting section 47.
With an input of the target vehicle speed VT, the target vehicle speed correcting section 47 determines a corrected target vehicle speed VAT by causing a controlgain multiplying section 49 to multiply a difference (VT-V) between the target vehicle speed VT and the actual vehicle speed V detected by thevehicle speed sensor 36 by a control gain k1 and adding the resulting correction amount k1 × (VT-V) to the target vehicle speed VT. - That is, the corrected target vehicle speed VAT is determined based on the following expression (1):
The corrected target vehicle speed VAT thus obtained is outputted to the state quantity computing section 48. With an input of the corrected target vehicle speed VAT, the state quantity computing section 48 computes a target engine rotation speed ωe,T and a target transmission input torque TTRN,T, on the basis of the corrected target vehicle speed VAT, which impart theengine 2 with the maximum efficiency. - More specifically, the state quantity computing section 48 includes a post-correction target engine
output computing section 50, a target engine rotation speed/target enginetorque computing section 51 serving as a target engine performance computing section, and a target transmission inputtorque computing section 52.
With an input of the corrected target vehicle speed VAT, the post-correction target engineoutput computing section 50 computes a post-correction target engine output Pe,AT for the corrected target vehicle speed VAT by employing the aforementionedfirst engine map 71. That is, a boosted target engine output is provided. - The computed post-correction target engine output Pe,AT is outputted to the target engine rotation speed/target engine
torque computing section 51. With an input of the post-correction target engine output Pe,AT, the target engine rotation speed/target enginetorque computing section 51 computes the target engine rotation speed ωe,T and a target engine torque Te,T by employing the aforementionedsecond engine map 72. At this time, the computation of the target engine rotation speed ωe,T and the target engine torque Te,T is based on the peak efficiency curve (PEC), thereby making it possible to effectively perform the drive control for improving the mileage without impairing the acceleration performance. - The target engine rotation speed ωe,T and the target engine torque Te,T computed by the target engine rotation speed/target engine
torque computing section 51 are outputted to the target transmission inputtorque computing section 52, while the computed target engine rotation speed ωe,T is outputted to theengine control section 44.
With inputs of the target engine rotation speed ωe,T and the target engine torque Te,T, the target transmission inputtorque computing section 52 computes the target transmission input torque TTRN,T by employing the following expression (2): -
The target transmission input torque TTRN,T is obtained from the expression (2).
Referring now toFig. 5 , theIVT control section 43 includes a real transmission inputtorque computing section 53, a target transmission inputtorque correcting section 54 serving as a CVT torque control section, a demanded pressuredifference computing section 55, asignal outputting section 56 and amode switching section 76. - The
mode switching section 76 computes an IVT gear ratio on the basis of the CVT input shaft rotation speed ωi (equivalent to the IVT input shaft rotation speed) detected by the CVT input shaftrotation speed sensor 38 and the IVT output shaft rotation speed ωIVT,o detected by the IVT output shaftrotation speed sensor 75, and outputs the coupling/decoupling command signals to the powercirculation mode clutch 27 and the direct mode clutch 29 on the basis of the computed IVT gear ratio for the mode switching. - With inputs of the CVT input shaft rotation speed ωi detected by the CVT input shaft
rotation speed sensor 38, the CVT output shaft rotation speed ωo detected by the CVT output shaftrotation speed sensor 39 and the pressure difference P between the first and secondhydraulic chambers pressure sensor 40, the real transmission inputtorque computing section 53 computes a real transmission input torque TTRN,R (for the direct mode) on the basis of the following expression (3): -
- kr:
- geometrical constant
- Rv:
- CVT gear ratio (Rv = ωo/ωi)
- ωi:
- CVT input shaft rotation speed
- ωo:
- CVT output shaft rotation speed
- That is, the corrected target transmission input torque TTRN,AT is determined on the basis of the following expression (4):
With an input of the corrected target transmission input torque TTRN,AT computed by the target transmission inputtorque correcting section 54 and with inputs of the CVT input shaft rotation speed ωi and the CVT output shaft rotation speed ωo for computation of the gear ratio Rv of the CVT 6, the demanded pressuredifference computing section 55 computes a demanded pressure difference PD to be applied between the first and secondhydraulic chambers -
With an input of the demanded pressure difference PD computed by the demanded pressuredifference computing section 55, thesignal outputting section 56 converts the demanded pressure difference PD into a voltage command signal, and outputs the voltage command signal to the solenoids of the firstpressure control valve 31 and the secondpressure control valve 33. Thus, desired reaction forces are applied to therollers - Referring next to
Fig. 6 , theengine control section 44 includes a real transmission inputtorque computing section 59, a demanded enginetorque setting section 60 and asignal outputting section 61.
With inputs of the CVT input shaft rotation speed ωi detected by the CVT input shaftrotation speed sensor 38, the CVT output shaft rotation speed ωo detected by the CVT output shaftrotation speed sensor 39 and the pressure difference P between the first and secondhydraulic chambers pressure sensor 40, the real transmission inputtorque computing section 59 computes the real transmission input torque TTRN,R on the basis of the above expression (3) . The computed real transmission input torque TTRN,R is outputted to the demanded engine torque computing {setting}section 60. - With inputs of the real transmission input torque TTRN,R, the target engine rotation speed ωe,T from the target engine rotation speed/target engine
torque computing section 51 of the driver'sdemand converting section 42 and the engine rotation speed ωe detected by the enginerotation speed sensor 37, the demanded enginetorque setting section 60 sets an engine torque Te computed from the following expressions (6-1) and (6-2) as a demanded engine torque Te,D (Te,D = Ie × k3 × (ωe,T - ωe) + TTRN,R). -
- Ie:
- engine inertia
- k3:
- control grain
- With an input of the demanded engine torque Te,D set by the demanded engine
torque setting section 60, thesignal outputting section 61 converts the demanded engine torque Te,D into a voltage command signal, and outputs a voltage command signal, for example, to the solenoid of the throttle valve aperture adjusting electromagnetic valve serving as the fuel supplyamount adjusting mechanism 41. This imparts theengine 2 with a desired dynamic characteristic.
In this embodiment, the control of the torque of theengine 2 is combined with the control of the transmission input torque which is a torque load exerted on theengine 2. This permits an optimum control operation. In other words, the optimum control operation is achieved by adding the control of the load torque exerted on the engine through the CVT 6 of the torque control type to the engine control. - More specifically, the relationship between the input and the output is linearized in the control by the
IVT control section 43 and the control by theengine control section 44, thereby simplifying the control operation. This reduces the costs and improves the power train response.
That is, where the CVT 6 of the torque control type is employed in a drive system such as the IVT adapted to control the power flow as in this embodiment, the engine inertia is separated from the vehicle inertia. Therefore, the engine torque Te does not directly influence the rotation speed of the vehicle wheels (substantially equivalent to the vehicle speed V). On the basis of such a premise, the power flow of the system is controlled by combining the torque control of the CVT 6 performed by theIVT control section 43 with the torque control of theengine 2 performed by theengine control section 44, and the above expression (6-1) based on the Newton' s second law is employed as a control rule. This makes it possible to determine the demanded engine torque Te,D without consideration of the vehicle inertia and adjust the engine output on the basis of the demanded engine torque Te,D. - Since the CVT 6 of the torque control type permits direct control of the input and output torques of the CVT 6, positive power flow from the
engine 2 to the vehicle wheels can be constantly maintained. That is, it is virtually ensured that the engine torque Te is maintained at a higher level than the real transmission input torque TTRN,R (Te > TTRN,R). - Therefore, the power flow from the
engine 2 to the drive wheels (positive flow with the engine torque Te kept at a higher level than the real transmission input torque TTRN,R, Te > TTRN,R) can be maintained in a transient drive control operation. That is, a so-called NMP (non-minimum phase) phenomenon can be prevented in which the rotation speed of the vehicle wheels otherwise initially suffers from undershoot in response to depression of an accelerator pedal. As a result, the drivability and the mileage are improved. - Since the
IVT control section 43 employs the single control gain k2 for the torque control of the CVT 6 and theengine control section 44 employs the single control gain k3 for the torque control of theengine 2, the control operation is simple and less expensive.
Further, theengine control section 44 serves to separate the engine response from the input torque (load) of the CVT 6 to linearize the engine speed response so that the response of the system linearly or monotonically increases (or decreases). This is advantageous in that the response of the rotation speed ωe of theengine 2 and the response of the rotation speed of the vehicle wheels (substantially equivalent to the vehicle speed V) are stabilized irrespective of the control gains k2, k3. - The demanded pressure
difference setting section 55 determines the demanded pressure difference PD on the basis of the above expression (5), i.e., PD = TTRN,AT × (1-Rv)/C. Therefore, a relationship between the demanded pressure difference PD and the corrected target transmission input torque TTRN,AT is linearized, and a relationship between the demanded pressure difference PD and the CVT gear ratio Rv is linearized, thereby simplifying the computation of the demanded pressure difference PD.
More specifically, the demanded pressure difference PD is increased and reduced according to the transmission gear ratio Rv of the CVT 6, and is increased and reduced proportionally to the target transmission input torque TTRN,AT. Therefore, the computation of the demanded pressure difference PD is very simple. - Further, a driver's demand applied to the motor vehicle through the accelerator pedal is converted into the state quantities, i.e., the target engine rotation speed ωe,T and the target transmission input torque TTRN,T, which impart the
engine 2 with the maximum efficiency, by the function of the driver'sdemand converting section 42. Thus, theengine 2 can be operated at the highest possible efficiency according to the driver's demand without impairing the acceleration performance of the motor vehicle. As a result, the mileage and the drivability are well-balanced. - In the driver's
demand converting section 42, the target vehicle speed correcting section 47 corrects the target vehicle speed VT on the basis of the comparison between the target vehicle speed VT and the actual vehicle speed V, whereby the engine power is artificially boosted according to the driver's demand. Particularly, the target vehicle speed VT is corrected by comparing the actual vehicle speed V with the target vehicle speed VT, more specifically, by employing the difference (VT - V) between the target vehicle speed VT and the actual vehicle speed V, so that the size of a control loop can be reduced. - In the target vehicle speed correcting section 47, the correction amount k1 × (VT - V) determined by multiplying the difference (VT-V) between the target vehicle speed VT and the actual vehicle speed V by the predetermined gain k1 is added to the target vehicle speed VT to provide the corrected target vehicle speed VAT. Since the single gain k1 is thus employed, the tuning of transient characteristics is facilitated in the power control of the
engine 2. Further, the control loop is simple and less expensive. In other words, a transmission kick-down function can be provided at lower costs. - In the driver' s
demand converting section 42, the target vehicle speed VT is corrected according to the driver's demand, and the target engine output is corrected on the basis of the corrected target vehicle speed VAT. Therefore, the engine output is boosted according to the driver's demand. The target level of the engine output to be boosted (the target engine rotation speed ωe,T and the target engine torque Te,T) is computed on the basis of the peak efficiency curve (PEC) for the relationship between the engine rotation speed ωe and the engine torque Te. This effectively improves the mileage without impairing the acceleration performance. - Of the above expressions (1) to (6-1), the expressions (1), (2), (4) and (6-1) are applicable to both the direct mode and the power circulation mode, and the expressions (3) and (5) are applicable to the direct mode.
Figs. 7 to 10 illustrate another embodiment of the present invention. This embodiment is directed to a vehicle drive control device including a CVT of a torque control type which does not constitute an IVT, while the previous embodiment ofFigs. 1 to 6 is directed to the vehicle drive control device having the IVT. - Referring to
Fig. 7 , this embodiment principally differs from the embodiment ofFig. 1 in that theplanetary gear mechanism 7, theIVT output shaft 8, thegear trains circulation mode clutch 27, thedirect mode clutch 29 and the IVT output shaftrotation speed sensor 75 are eliminated. ACVT output shaft 10 is coupled to drivewheels 83 through agear train 80, adifferential device 81 and adrive shaft 82. Thegear train 80 includes agear 80a corotatable with theCVT output shaft 10, and agear 80b meshed with thegear 80a and corotatable with a case of thedifferential device 81. - Referring to
Fig. 8 , acontroller 34A of this embodiment principally differs from thecontroller 34 of the embodiment ofFig. 3 in that aCVT control section 43A is provided instead of theIVT control section 43. In this embodiment, a target transmission input torque TTRN,T to be applied to theCVT control section 43A from a driver'sdemand converting section 42 is equivalent to a target CVT input torque.
Referring toFig. 9 , the target transmission input torque TTRN,T is computed by a target transmission inputtorque computing section 52 of the driver'sdemand converting section 42 of thecontroller 34A of this embodiment, and applied to theCVT control section 43A. - Referring to
Fig. 10 , theCVT control section 43A of this embodiment principally differs from theIVT control section 43 ofFig. 5 in that themode switching section 76 is eliminated. In this embodiment, a real transmission input torque TTRN,R computed by a real transmission inputtorque computing section 53 ofFig. 10 is equivalent to the real CVT input torque (actual CVT input torque). - In this embodiment, an
engine control section 44 has the same construction as in the embodiment ofFig. 6 .
This embodiment provides the same functions and effects as the embodiment ofFigs. 1 to 6 , so that the mileage and the drivability are well-balanced.
It should be understood that the present invention be not limited to the embodiments described above. Theplanetary gear mechanism 7 is simply required to include an element coupled to theCVT input shaft 9, an element coupled to theCVT output shaft 10 and an element coupled to the drive wheels. Further, at least one of thegear trains - With a control system having the same construction as in
Figs. 1 to 6 , the engine output was boosted with the control gain k1 set at a relatively low level in the target vehicle speed correcting section 47 ofFig. 4 in Example 1, and the engine output was boosted with the control gain k1 set at a relatively high level in Example 2. In Comparative Example 1, the target vehicle speed correcting section was eliminated. A simulation was performed to determine a response time from the operation of the accelerator pedal to the start of a vehicle speed change. The results are shown inFig. 11 . - The test results prove that Examples 1 and 2 in which the engine output was boosted by correcting the target vehicle speed according to the driver's demand are much more excellent in responsiveness than Comparative Example 1.
While the present invention has thus been described in greater detail by way of the specific embodiments, those skilled in the art who have understood the foregoing will easily come up with variations, modifications and equivalents of the embodiments. Therefore, the scope of the present invention is defined by the appended claims and their equivalents. - This application corresponds to the following applications filed in the Japanese Patent Office:
- Application No.
2005-289085 (filed on September 30, 2005 - Application No.
2006-099806 (filed on March 31, 2006 - Application No.
2006-099807 (filed on March 31, 2006 - Application No.
2006-099808 (filed on March 31, 2006 - Application No.
2006-221231 (filed on August 14, 2006 - Application No.
2006-221232 (filed on August 14, 2006 - Application No.
2006-221233 (filed on August 14, 2006
Claims (16)
- A vehicle drive control device comprising:- a continuously variable transmission mechanism CVT of a torque control type capable of continuously varying a transmission gear ratio; and- a controller (34) which controls operations of the CVT (6) and an engine (2);- wherein the controller (34) includes a first control section (43) which controls a torque of the CVT (6) based on a target transmission input torque TTRN,T, and a second control section (44) which controls a torque of the engine (2) based on a target engine rotation speed ωe,T,- wherein the controller (34) which controls the operations of the CVT (6) and the engine (2) includes a driver's demand converting section (42) which determines a state quantity which provides a vehicle driving state demanded by a driver;- wherein the driver's demand converting section (42) computes a target engine rotation speed ωe,T and a target transmission input torque TTRN,T which impart the engine (2) with a maximum efficiency as the target engine rotation speed ωe,T and the target transmission input torque TTRN,T based on an accelerator operation amount (θ) detected by accelerator operation amount detecting means (35) and a vehicle speed (V) detected by vehicle speed detecting means (36);- characterised in that the driver's demand converting section (42) further includes:-- a target vehicle speed computing section (46) which computes a target vehicle speed based on the detected accelerator operation amount θ and the detected vehicle speed V;-- a target vehicle speed correcting section (47) which corrects the target vehicle speed based on a comparison between the target vehicle speed computed by the target vehicle speed computing section (46) and the detected vehicle speed V to provide a corrected target vehicle speed; and-- a state quantity computing section (48) which computes the target engine rotation speed ωe,T and the target transmission input torque TTRN,T based on the corrected target vehicle speed.
- The control device according to claim 1,
wherein the CVT (6) includes:- an input disk (11, 12) and an output disk (13, 14) biased toward each other;- a roller (15, 16) disposed in a toroidal space defined between the input disk (11, 12) and the output disk (13, 14) for torque transmission between the input disk and the output disk;- a carriage (17) rotatably supporting the roller (15, 16); and- a hydraulic cylinder (19) having first and second hydraulic chambers (20, 21) which generate a pressure difference to apply a force to the roller (15, 16) through the carriage (17) for pushing and pulling the input disk (11, 12) and the output disk (13, 14);- wherein the first control section (43) includes a demanded pressure difference setting section (55) which determines a demanded pressure difference PD between the first and second hydraulic chambers (20, 21) to eliminate a difference between the target transmission input torque TTRN,T and an actual transmission input torque TTRN,R. - The control device according to claim 2,
wherein the first control section (43) further includes a target transmission input torque correcting section (54) which corrects the target transmission input torque TTRN,T to eliminate the difference between the target transmission input torque TTRN,T and the actual transmission input torque TTRN,R,
wherein the demanded pressure difference setting section (55) determines the demanded pressure difference PD based on a corrected target transmission input torque TTRN,AT applied from the target transmission input torque correcting section (54). - The control device according to claim 3,
wherein the demanded pressure difference setting section (55) determines the demanded pressure difference PD based on the following expression:
whereinTTRN,AT: corrected target transmission input torquekr: geometrical constantRv: CVT gear ratio (Rv = ωo/ωi)ωi: CVT input shaft rotation speedωo: CVT output shaft rotation speed - The control device according to claim 3,
wherein the demanded pressure difference PD is increased and reduced according to a CVT gear ratio RV, and is increased and reduced proportionally to the corrected target transmission input torque TTRN,AT· - The control device according to claim 1,
wherein the second control section (44) includes a demanded engine torque setting section (60) which sets an engine torque Te computed based on the following expression as a demanded engine torque Te,D:
whereinIe: engine inertiak3: control grain(ωe,T: target engine rotation speedωe: actual engine rotation speedTTRN,R: actual transmission input torque - The control device according to claim 6,
wherein a power flow between the engine (2) and a drive wheel is controlled so that the engine torque Te is greater than an actual transmission input torque TTRN,R acting as an engine load. - The control device according to claim 6,
wherein the second control section (44) further includes a target engine rotation speed computing section (51) which computes the target engine rotation speed ωe,T based on a detected accelerator operation amount (θ) and a detected vehicle speed V. - The control device according to claim 6,
wherein the CVT (6) includes:- an input disk (11, 12) and an output disk (13, 14) biased toward each other;- a roller (15, 16) disposed in a toroidal space defined between the input disk (11, 12) and the output disk (13, 14) for torque transmission between the input disk and the output disk;- a carriage (17) rotatably supporting the roller (15, 16); and- a hydraulic cylinder (19) having first and second hydraulic chambers (20, 21) which generate a pressure difference to apply a force to the roller (15, 16) through the carriage (17) for pushing and pulling the input disk (11, 12) and the output disk (13, 14);- wherein the first control section (43) includes a real transmission input torque computing section (59) which computes an actual transmission input torque TTRN,R;- wherein the real transmission input torque computing section (59) computes the actual transmission input torque TTRN,R based on detected rotation speeds ωi, ωo of the input disk (11, 12) and the output disk (13, 14) or parameters equivalent to the rotation speeds and a detected pressure difference between the first and second hydraulic chambers (20, 21) or a parameter equivalent to the pressure difference. - The control device according to claim 1,
wherein the target vehicle speed correcting section (47) adds a correction amount obtained by multiplying a difference between the target vehicle speed computed by the target vehicle speed computing section (46) and the detected vehicle speed V by a predetermined gain to the target vehicle speed to provide the corrected target vehicle speed. - The control device according to claim 1,
wherein the state quantity computing section (48) includes:- a target engine performance computing section (50, 51) which computes a target engine rotation speed ωe,T and a target engine torque Te,T which impart the engine (2) with the maximum efficiency based on an engine output associated with the corrected target vehicle speed VAT; and- a target transmission input torque computing section (52) which computes the target transmission input torque TTRN,T based on the target engine rotation speed ωe,T and the target engine torque Te,T computed by the target engine performance computing section (50, 51). - The control device according to claim 11,
wherein the target transmission input torque TTRN,T computed by the target transmission input torque computing section (52) is output to the first control section (43). - The control device according to claim 11,
wherein the target engine rotation speedy ωe,T omputed by the target engine performance computing section (50, 51) is output to the second control section (44). - The control device according to claim 12,
wherein the CVT (6) includes a CVT of a full-toroidal type. - The control device according to claim 1,
wherein the driver's demand converting section (42) determines the target transmission input torque TTRN,T and the target engine rotation speed ωe,T as the state quantity,
wherein the target transmission input torque TTRN,T determined by the driver's demand converting section (42) is output to the first control section (43),
wherein the target engine rotation speed ωe,T determined by the driver's demand converting section (42) is output to the second control section (44). - The control device according to any one of claims 1 to 15,
further comprising an infinitely variable transmission IVT (1) capable of providing a state having an infinite transmission gear ratio,
wherein the IVT (1) includes:- the CVT (6);- a planetary gear mechanism (7) disposed between an input shaft (9) and an output shaft (10) of the CVT (6);- a power circulation mode clutch (27) to be coupled when a power circulation mode is implemented to achieve power transmission within a transmission gear ratio range including the infinite transmission gear ratio; and- a direct mode clutch (29) to be coupled when a direct mode is implemented to achieve the power transmission by the CVT (6) alone.
Applications Claiming Priority (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005289085 | 2005-09-30 | ||
JP2006099808 | 2006-03-31 | ||
JP2006099807 | 2006-03-31 | ||
JP2006099806 | 2006-03-31 | ||
JP2006221232A JP5225563B2 (en) | 2006-03-31 | 2006-08-14 | Vehicle drive control device |
JP2006221231A JP5071704B2 (en) | 2006-03-31 | 2006-08-14 | Vehicle drive control device |
JP2006221233A JP4873235B2 (en) | 2005-09-30 | 2006-08-14 | Vehicle drive control device |
PCT/JP2006/319418 WO2007040164A1 (en) | 2005-09-30 | 2006-09-29 | Drive control device for vehicle |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1930221A1 EP1930221A1 (en) | 2008-06-11 |
EP1930221A4 EP1930221A4 (en) | 2011-04-13 |
EP1930221B1 true EP1930221B1 (en) | 2013-03-27 |
Family
ID=37906206
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06810824A Expired - Fee Related EP1930221B1 (en) | 2005-09-30 | 2006-09-29 | Drive control device for vehicle |
Country Status (4)
Country | Link |
---|---|
US (1) | US8088036B2 (en) |
EP (1) | EP1930221B1 (en) |
CN (1) | CN101312867B (en) |
WO (1) | WO2007040164A1 (en) |
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- 2006-09-29 CN CN200680043908.4A patent/CN101312867B/en not_active Expired - Fee Related
- 2006-09-29 US US11/992,761 patent/US8088036B2/en not_active Expired - Fee Related
- 2006-09-29 EP EP06810824A patent/EP1930221B1/en not_active Expired - Fee Related
- 2006-09-29 WO PCT/JP2006/319418 patent/WO2007040164A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
CN101312867A (en) | 2008-11-26 |
EP1930221A1 (en) | 2008-06-11 |
CN101312867B (en) | 2012-07-04 |
WO2007040164A1 (en) | 2007-04-12 |
US20090143192A1 (en) | 2009-06-04 |
US8088036B2 (en) | 2012-01-03 |
EP1930221A4 (en) | 2011-04-13 |
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